Isothermal-turbo-compressor-expander-condenser-evaporator device

ABSTRACT

This invention provides an isothermal turbo-compressor-expander-condenser-evaporator in a single integral arrangement that is suitable for a variety of compact arrangements, such as a window air-conditioner and/or automotive-based unit. This arrangement avoids the use of rotary fluid joints and maintains the entire fluid cycle, including compression, condensation, expansion and evaporation within a single rotating shaft-based structure, with the compressor/condenser section and the expansion/evaporator section separated from each other in separate spaces and/or plena by a rotating, insulated barrier disc and associated seal.

RELATED APPLICATION

This application claims the benefit of co-pending U.S. ProvisionalApplication Ser. No. 62/080,996, entitledISOTHERMAL-TURBO-COMPRESSOR-EXPANDER-CONDENSER-EVAPORATOR DEVICE, filedNov. 17, 2015, the entire teaching of which is expressly incorporatedherein by reference.

FIELD OF THE INVENTION

This invention relates to air conditioning, heating, heat pumps,refrigeration, and similar heat-exchange devices, and more particularlyto devices capable of being contained in a limited space

BACKGROUND OF THE INVENTION

A disadvantage to conventional air-conditioning and heat pumparrangements that employ an evaporative/condensing, phase-changingcompound, such as refrigerant arrangement is that they require acompressor to first pressurize the refrigerant so that it becomes ahigh-pressure, heated gas, a condenser for providing the heat exchangerequired to cool down the refrigerant before it passes into the coilwithin the refrigerant compartment, and an expansion valve. Thistypically requires the use of three separate and discrete devices, onefor performing each process within the air-conditioning/refrigerationcycle, all interconnected by fluid-tight appropriate tubing. Thisreduces efficiency and increases component count and cost. Moreparticularly, it is a well-established principle of thermodynamics that,at identical pressures, more energy is required to compress a gas at ahigher temperature than the same gas at a lower temperature. Thus,compression with delay of heat expulsion until completion of thecompression requires more energy than compression with anticipated heatexpulsion during the compression. The ability to implement this processin a more-isothermal manner, in which heat is removed from therefrigerant concurrently with the compression, can provide amore-efficient overall cycle.

Various systems have attempted to overcome the various disadvantages ofa conventional air conditioning, refrigeration and/or heat pumparrangement, including providing systems having multi-stage compressioncomponents separated by intermediate cooling stages; and/or systems withexpansion through a turbine sharing a rotating shaft with thecompressor. However, these systems typically require an increasedcomponent count relative to a conventional arrangement—for example afirst-stage compressor, flash chamber, heat exchanger, and second-stagecompressor. These multi-stage systems have typically been limited tolarge-scale refrigeration systems due to the number of components (andassociated higher cost) required for operation. This cost and complexityrenders such systems, undesirable for smaller scale air-conditioning andrefrigeration applications, or those deployed in a relatively confinedspace, such as a window air conditioner, or automotive air conditioningsystem.

In other prior art arrangements, piston-type compressors are providedthat include cooling jackets that remove heat from the compressor wallto enhance isothermalism, and/or intermediate heat exchangers betweenthe stages of a multi-stage compressor assembly. However, thesecompressors operate with a reciprocating piston that does not allowsufficient physical proximity between the refrigerant under compression(inside the piston chamber) and the fluid (such as atmospheric air) usedfor the cooling, and only a fraction of the heat can be extracted duringthe compression. Thus, these (and other prior art systems) do not allowfor a large portion of cooling (and condensation) to desirably occurduring the compression cycle to improve efficiency.

Commonly assigned U.S. Pat. No. 8,578,733 (hereinafter '733), entitledTURBO-COMPRESSOR-CONDENSER-EXPANDER, which is herein incorporated byreference as useful background information, describes a refrigeration,air-conditioning and heat-transfer system that overcomes variousdisadvantages of conventional and prior art arrangements, by providing adevice that reduces the number of interconnected, discrete components soas to provide for increased fluid-tightness over a long service life, aswell as potentially reduced production costs and increases overallreliability. This system provides a single apparatus capable ofperforming simultaneous refrigerant compression, condensation, andexpansion, thereby improving efficiency and overall design ofair-conditioning, refrigeration and heat-pumping systems.

The '733 patent discloses a design for a highly efficient isothermalturbo-compressor-condenser-expander, that employs rotary fluid unions tointerface the rotating components with the stationary components of therefrigeration apparatus. In various implementations, rotary fluid unionscan incur additional frictional losses and potentially pose a leak pointfor emissions of environmentally deleterious refrigerants if they areutilized. Such rotary fluid unions may also limit the maximum operatingpressures for refrigerant fluids, and hence can limit potentialrefrigerant selection to those with greater-than-ambient absolutepressure while operating to prevent leaks inward with resultantrefrigerant contamination.

Additionally, the devices described in the '733 patent may be directedmore toward a limited number of operating points over a range ofrefrigeration capacity, making this arrangement less-suited to certainimplementations in which a wide operating range is desired (e.g. windowair conditioners and automotive units). The refrigeration processdisclosed in the '733 patent is also inherently limited from reachingthe maximum efficiency possible, as the pressure range over which therefrigerant is expanded isentropically does not have much work availabledue to a limited change in volume.

Thus, it is desirable to provide various improvements to theimplementation of '733 to more closely realize its full potential forimproved energy efficiency, and confer additional practical advantagesin implementation.

SUMMARY OF THE INVENTION

This invention overcomes disadvantages of prior art by providing anisothermal turbo-compressor-expander-condenser-evaporator in a singleintegral arrangement that is suitable for a variety of compactarrangements, such as a window air-conditioner and/or automotive-basedunit. This arrangement avoids the use of rotary fluid joints andmaintains the entire fluid cycle, including compression, condensation,expansion and evaporation within a single rotating shaft-basedstructure, with the compressor/condenser section and theexpansion/evaporator section separated from each other in separatespaces and/or plena by a rotating, insulated barrier disc and associatedseal.

In an illustrative embodiment, aturbo-compressor-condenser-expander-evaporator (TCCEE) for a refrigerantis provided. A central axis assembly, including a first compressorstage, provides isentropic adiabatic mechanical compression in therefrigerant, and a second compressor stage, provides isothermalcentrifugal compression in radially expanding refrigerant-filledconduits. The conduits are arranged in surfaces to induce heat transferand a first air flow to remove heat of compression and condensation. Thecentral axis assembly further includes an expander and evaporator stage,receiving the compressed and condensed refrigerant from the secondcompression stage. It provides isentropic centrifugal expansion andisothermal expansion and evaporation in radially contracting conduits.The conduits are arranged to induce a second air flow over surfaces ofthe condenser and evaporator. A prime mover rotates the central axialassembly to supply energy sufficient to compress refrigerant andcirculate the first air flow and the second air flow through the device.Illustratively, a stationary plenum collects and directs the second airflow by the rotating action of the surfaces of the condenser andevaporator. The surfaces of the condenser and evaporator definegenerally blade-shaped conduits carrying refrigerant therein. Further,an insulated barrier disc can be attached to the central axle axialassembly and closely fit to the stationary plenum to minimize airleakage between the insulated barrier disc and the stationary plenum. Anadditional stationary plenum can be arranged around the surfaces of thecompressor and condenser to collect and direct the air warmed bycompression and condensation.

In embodiments, a diverter assembly can be operatively connected witheach of the stationary plenum and the additional stationary plenum. Thisdiverter assembly, in conjunction with the plena, is constructed andarranged so that a destination and a source of hot air and cold air areinterchangeable. In embodiments, the compressor includes a compressorshaft and a compressor shaft anchor attached to an independent motorshaft of the prime mover. The compressor shaft anchor can be interfacedinto a planetary gear transmission driven from a central axial shaft todrive the compressor shaft at a speed multiple of the central axialshaft. Illustratively, the first compressor stage can comprise ashaft-driven mechanical compressor coupled through a sealed shaft ormagnetic coupling attached to a stationary anchor and the mechanicalcompressor can comprise a digital scroll compressor in which the primemover (drive motor) rotates at a constant speed.

In illustrative embodiments, a housing encloses the components, in whichthe housing defines a window-mounted air conditioning unit.

In various embodiments, the refrigerant can comprises ahigh-molecular-weight refrigerant working fluid with less thanatmospheric pressure compressor suction conditions, and moreparticularly R-123 and/or “hydrofluoroolefin analogues: intended forcentrifugal compressors. Such analogues can include, but are not limitedto DR-2, HFO1234yf, and DR-11, (e.g.) HFO1234ze and similar compounds,as well as those that can be developed in the future, from suchwell-known international maufacturers, such as Honeywell and DuPont.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention description below refers to the accompanying drawings, ofwhich:

FIG. 1 is a fragmentary perspective view of an isothermalturbo-compressor-compressor-condenser-expander-evaporator (ITCCEE)according to an illustrative embodiment;

FIG. 2 is a side cross section of the ITCCEE according to FIG. 1;

FIG. 3 is a graph taken along temperature and entropy axes of a reversedCarnot cycle with wet adiabatic compression;

FIG. 4 is a graph taken along temperature and entropy axes of a reversedCarnot cycle with dry compression, wet isothermal compression andcondensation as provided by the device of FIGS. 1 and 2;

FIG. 5 is a flow circuit diagram of a device employing an idealCarnot-type cycle; and

FIG. 6 is a schematic diagram of a reversible heat-pump-type system inwhich diverters and plenums are selectively controlled to provideheating or cooling to a selected space based on the flow of air througheither the compressor/condenser section or the expander/evaporatorsection, respectively.

DETAILED DESCRIPTION I. ITCCEE Structure and Operation

Reference is made to an isothermalturbo-compressor-condenser-expander-evaporator (ITCCEE) device 100 shownin FIGS. 1 and 2. Similar to the above-incorporated '733 patent,describing an isothermal turbo-compressor-condenser-expander ITCCE, theillustrative ITCCEE is comprised as a rotating air-heat exchange devicein which components of the heat-exchange cycle are contained integrallyon the same rotating drive shaft. Notably, the illustrative embodimentof the ITCCEE is free of rotary fluid unions for increased reliability,and efficiency. To eliminate the use of rotary fluid unions, thepositive displacement precompressor and evaporator are repositioned andintegrated with the overall rotating, central axial assembly.

In this embodiment, the device 100 includes a drive shaft 110 that isoperatively connected by any acceptable power transmission assembly to adrive motor 210 that rotates (curved arrow R) the shaft at a fixed, ortypically, variable speed, based upon a motor controller 212. The motor210 and controller 212 can be connected to a battery or wall-outletpower source or can be rotatably driven by another form of drive such asan internal combustion engine, wind/water turbine, or vehicle drivetrain. The drive shaft 110 can be supported in a frame or housing byappropriate rotary bearings (not shown). The drive shaft is hollow,including an axially-oriented lumen 112 along at least a portion 114 ofthe shaft 110 as shown. This lumen 112 allows fluid to be carriedaxially (i.e. on shaft axis SA) along the rotating assembly.

Illustratively, a shaft-mounted precompressor 120 draws low pressurerefrigerant vapor through the hollow portion 114 of the shaft 110, anddischarges it at intermediate pressure into a toroidal inner plenum 130that surrounds the precompressor 120. The inner plenum interconnects anarrangement of radially aligned spokes that are defined by axiallytwisted blades/conduits 140 (twisted about a longitudinal/elongationaxis). The conduits 140 each carry one or more conduits that allowpassage of liquid therealong as air is biased axially and radially(airflow arrow AF1) over the conduits 140 in response to their rotationand associated twist geometry. This airflow passage causes cooling ofthe precompressed fluid as well as additional compression in response tothe centripetal force generated by rotation. Thus, the conduits act ascompressors and condensers within the condenser section/space 220 of thedevice 100. This function, and associated blade structures, are bothdescribed further in the above-incorporated '733 patent. The compressedand condensed fluid is directed radially outwardly along a distance R1into a toroidal outer plenum 150 where it intermixes and thepressure/flow or the fluid is equalized. Note that the conduits can beconstructed as a symmetrical-cross-section or asymmetrical-cross-section(e.g. airfoil) shape using, for example extrusion techniques in which aplurality of ports are formed down the elongated length of the conduit.The multiple ports carry the fluid between the plenums 130, 150 andafford greater surface contact between the fluid and conduit material(e.g. aluminum alloy with brazed plenum joints) for more-efficient heatexchange with the ambient air (airflow AF1) passing over the conduits140. The construction of multi-port conduit extrusions, toroidal plenumsand other structures described herein is shown and described, by way ofnon-limited example, in commonly assigned U.S. patent application Ser.No. 14/543,868, filed Nov. 17, 2014, entitledTURBO-COMPRESSOR-CONDENSER-EXPANDER, the teachings of which areexpressly incorporated herein by reference.

Thus, the plenum-interconnecting, axially twisted (along an elongationdirection/longitudinal axis) conduit extrusions (in the manner of ahelix) serve as flow conduits radially outwardly, and comprise thecompressor/condenser heat exchange surface that also serves to induce aflow of air by its combined axial and radial fan characteristics whenrotated. The precompressor 120 can be constructed using a variety ofknown arrangements, including a scroll, rotary, axial piston or othersuitable type of adiabatic gas compressor. As described generally above,in various embodiments, the precompressor 120 can be driven by a motor(210) comprising a mechanically sealed shaft drive connected to astationary fixture/frame (not shown in FIGS. 1 and 2), a separate motorshaft (as shown and described in the '733 patent), a magnetic coupling,and/or ‘canned’ electrical armature surrounded by stator wiring.

The fluid path of compressed, condensed refrigerant through the extrudedconduits is collected in the outer toroidal plenum 150, and thendirected through a plurality of axially parallel conduits 160 arrangedaround the perimeter of the device, which pass through a plurality ofcorresponding slots 162 in a barrier disc 170 that rotates with theshaft 110. The barrier disc 170 deflects the airflow (arrow AF1) fromentering the evaporator section/space 230 of the device, thus isolatingthe ambient air from the evaporator and cooled space airflow (arrowsAF2). The outer edge 172 of the barrier disc 170 seats within a sealingrecess (e.g. a loose seal) 242 in a fixed drum-shaped cold air plenum240. The fluid then passes from the axial conduits 160 around a rightangle bend 166 into a plurality of radially inwardly directed, unitary(or integral) conduit sections 168 that can be constructed as multiportplanar extrusions. These lead into integral tubular sections 180 thatjoin axially directed conduits 182 that can be constructed as multiportextrusions. In this location, the fluid is isentropically and,subsequently, isothermally expanded as the liquid refrigerant is reducedin pressure and evaporates (i.e. an expander/evaporator section of thedevice, contained within the cold air plenum space 230.

The expander/evaporator heat exchange surface, comprised of planarmultiport conduit extrusions 182, also serves to induce a flow of air(arrows AF2) in the manner of a radial ‘squirrel cage’ blower due totheir radially aligned geometry. Note that a different conduitblade-cross-section geometry can be employed where airflow (arrows AF2).The air flows from the cooled space (e.g. a room or crew compartment)through an axially aligned intake 250 in the cold air plenum 240, overthe rotating expander/evaporator conduits 182 and out an outlet 260,located along a portion of the plenum surface, where the cooled air isreturned back into the cooled (room) space.

The evaporator superheats the exiting refrigerant vapor via heatexchanged with warm intake airflow from the cooled space which is thenreturned down a corresponding radially inwardly directed tubes 184 overa radial distance R2 to a central hub 190 rotating on the hollow shaftsection 114 about the axis SA. Thus the fluid passes through the shaftlumen 112 under precompressor suction back to the precompressor 120.

In an illustrative embodiment, the evaporator section/space 230 iscontained within a stationary cold air plenum 240, interfaced with abarrier disc 170. The barrier disc 170 can be layered with a suitablyinsulating material, and as described above, is sealed around the discperimeter 172 against substantial air leakage with suitablestructures/techniques such as close mechanical fit into a plenum slot242, labyrinth or whisker seals, or any other suitable structure ortechnique for sealing two rotating surfaces against excessive airpassage therebetween. The condenser section 220 is shown as an opensystem, but optionally can also be contained within a separate airplenum 262 (shown in phantom) that can be part of an overall housing(e.g. the outer housing 200 (shown in phantom) of a window airconditioner), to direct the condenser side air flow (Arrow AF1), or tomaintain a state of equalized or nearly equalized pressure between theplenums to manipulate the direction and amount of leakage between themdown to zero as required, or a direction and amount to adjust the amountof fresh make up air, from the exterior ambient environment, andrelative humidity as desired.

As shown in FIG. 2, the dimensional characteristics of the compressorradius R1, the expansion length L, and the evaporator radius R2 can bemanipulated for the desired degree of compression and expansionappropriate for a selected refrigerant or process conditions,independent of rotational speed, and to facilitate the proper sizing ofheat transfer area between the condenser and evaporator surfaces, andthe air flow characteristics of the condenser and evaporator devices,addressing a limitation of the devices disclosed in the '733 patent.Appropriate sizing for a given heat-exchange task can be determinedbased upon empirical calculations known to those of skill and with theaid of trial and error experimentation by varying the lengths of variouscomponents and/or their volumetric/mass-flow carrying capacity.

II. Thermodynamic Process

The '733 patent discloses devices and a thermodynamic process that makesuse of the centrifugal field and the Coriolis force to conductsubstantially isothermal compression (or an endoreversible sequence ofadiabatic and isothermal compressions), and isentropic expansion. Thevarious embodiments of the device in the '733 patent provide aconfiguration that is tolerant of ‘wet’ expansion and relativelystraightforward to manufacture. However, the device falls short (as inall real processes) of the theoretical ideal minimum energy consumption,described by the reversed Carnot thermodynamic cycle (forrefrigeration).

It is an object of the present invention to more closely follow thereversed Carnot cycle and approach the theoretical efficiency desired inthe '733 patent device configuration. FIG. 3 depicts a graph 300 thereversed Carnot thermodynamic cycle in temperature (T) and entropy (S)coordinates. The steps of isentropic adiabatic compression occur onsegment 1-2, condensation on segment 2-3, isentropic expansion onsegment 3-4, and evaporation on segment 4-1. The net energy W^(•)required for the Carnot cycle conducted between Te and Tc is the areacontained within region 1-2-3-4, and the net refrigeration Q^(•)produced is the area beneath segment 1-4 extended to the origin. For anisentropic liquid expansion from 3 to 4, the amount of energy producedis the change in specific volume or ‘V dP work’. While the '733 patentdiscloses a device that can plausibly extract this energy, it is amodest amount when limited to only expansion of the condensed highpressure liquid refrigerant.

FIG. 4 shows a graph 400 depicting the same reversed Carnot cycle asthat of the graph 300 in FIG. 3, herein modified to avoid the presenceof liquid refrigerant in the isentropic compression step, which cancause mechanical difficulties to the illustrative configuration.Refrigerant vapor is compressed isentropically on segment 1 to 2, andcompressed isothermally on segment 2 to 3. Condensation occurs between 3and 4, followed by expansion between 4 and 5, and evaporation between 5and 1. Notably, this is the proposed path followed by the device andprocess in the '733 patent, with an adiabatic precompressor, followed byan isothermal compression and condensation, and then an isentropicexpansion stage. The net energy W^(•) between stage 3-4 can becharacterized by the following equation:

{dot over (W)}=∫ _(Pe) ^(Pc) {dot over (v)}dP

FIG. 5 shows a flow circuit diagram 500 of the devices and stepsnecessary to conduct the reversed Carnot cycle (See by way of usefulbackground Clausse et al., International Journal of Refrigeration 31(2008) 1190-1197. Significantly, the presence of an isothermal expansionstep provides additional cooling duty and energy output to supply afraction of the net work required to operate the compression.

The centrifugal field and Coriolis forces of the expanding refrigerant,and the increase in specific volume (and resultant acceleration andtorque) are as relevant and effective in the now-rotating evaporator ofthe illustrative embodiment herein as they are in the expander sectiondescribed in the '733 patent. Advantageously, the energy of expansion isnow more fully harvested to conduct the overall compression stepsrequired. The improved heat-transfer/exchange effects of the rotatingdevice and centrifugal field (film drainage, forced convection) presentfor the isothermal compressor and condenser section in the '733 patentare also conferred upon the evaporator of the illustrative embodiment.

The illustrative embodiment herein also reduces the number of primemovers required, in that a common shaft connected to as few as one motorserves to integrate the energy required to operate both compressionsteps as well as the fan pumping energy for the air flows in both thecondenser and evaporator, compared to as many as three motors for acondenser fan, evaporator air handler, and refrigerant compressor in aconventional vapor-compression refrigeration process.

While it is not the aim of the present invention to provide athermodynamic process for the transformation of heat into work, butrather that of work into heat flow from cold to hot, it is noted thatthis device has the potential to conduct the Carnot process to producemechanical work when energized in the manner of a turbine and heated bya source such as flue gas from a combustor, while rejecting heat to anatmospheric heat sink through an air-cooled condensing heat exchanger.

III. Reversible Heat-Pump-Type Device

The above-described illustrative embodiment is particularly suitable forswitching from heating to cooling, in the manner of a combined heatpump/air conditioning device, in that the air flow can be reversed fromindoors to out through ducts, plenums and diverters in a manner known tothose of skill, rather than reversing the refrigerant flow direction, asis commonly practiced. That is, the airflow of the indoor space can beexposed to the compressor/condenser section 220 in a heating cycle,while the external environment is exposed to the expander/evaporatorsection 230.

With reference to FIG. 6, a reversible heat-pump arrangement 600 isshown, in which a space (Space 1 or Space 2) can be provided with eithercooled air flow or warmed air flow based upon the selection of a uservia a control 610 that actuates a set of (e.g. electrically actuated)diverters (e.g. baffles) 620, 622, 624 and 626. These baffles arelocated at the inlet and outlet of each plenum. As depicted, baffles 620and 622 are located, respectively, at the inlet and outlet of thedevice's expander/evaporator section 630, whilst baffles 624 and 626 arelocated at the respective inlet and outlet of the compressor/condensersection 640. The baffles move synchronously between two opposingpositions to channel air from either Space 1 or Space 2, depending uponwhether cooling or heating is desired. In this manner the destinationand source of cold and hot air can be changed without (free of) changingthe running direction (rotation) of the device. Appropriate ducting andports to each space (e.g. indoors and outdoors) are provided and are notshown herein.

IV. Conclusion

It should be clear that the illustrate embodiment provides a highlyefficient and straightforward to manufacture/service heat-exchangedevice. The device can be scaled to operate in a wide range of differentapplications, and in particular to those benefitting from a selfcontained system with a minimal number of parts and prime movers, suchas a window air conditioning unit.

The foregoing has been a detailed description of illustrativeembodiments of the invention. Various modifications and additions can bemade without departing from the spirit and scope of this invention.Features of each of the various embodiments described above may becombined with features of other described embodiments as appropriate inorder to provide a multiplicity of feature combinations in associatednew embodiments. Furthermore, while the foregoing describes a number ofseparate embodiments of the apparatus and method of the presentinvention, what has been described herein is merely illustrative of theapplication of the principles of the present invention. For example, asused herein, terms such as “up”, “down”, “side”, “top”, “bottom”,“inside”, “outside”, and the like, are meant as conventions only and notas absolute directions/orientations. Also, it is expressly contemplatedthat the refrigerant used is highly variable and can include varioushydrofluoroolefin analogues. Such analogues can include, but are notlimited to DR-2, HFO1234yf, and DR-11, (e.g.) HFO1234ze and similarcompounds, as well as those that can be developed in the future, fromsuch well-known international manufacturers, such as Honeywell andDuPont. Accordingly, this description is meant to be taken only by wayof example, and not to otherwise limit the scope of this invention.

What is claimed is:
 1. A turbo-compressor-condenser-expander-evaporator(TCCEE) for a refrigerant comprising: a central axis assembly includinga first compressor stage that provides isentropic adiabatic mechanicalcompression in the refrigerant, and a second compressor stage, thatprovides isothermal centrifugal compression in radially expandingrefrigerant-filled conduits, the conduits being arranged in surfaces toinduce heat transfer and a first air flow to remove heat of compressionand condensation; the central axis assembly including an expander andevaporator stage, receiving the compressed and condensed refrigerantfrom the second compression stage, and that provides isentropiccentrifugal expansion and isothermal expansion and evaporation inradially contracting conduits, the conduits being arranged to induce asecond air flow over surfaces of the condenser and evaporator; and aprime mover to rotate the central axial assembly to supply energysufficient to compress refrigerant and circulate the first air flow andthe second air flow through the device.
 2. The TCCEE as set forth inclaim 1 further comprising a stationary plenum to collect and direct thesecond air flow by the rotating action of the surfaces of the condenserand evaporator, the surfaces of the condenser and evaporator definingblade-like conduits carrying refrigerant therein.
 3. The TCCEE as setforth in claim 2 further comprising an insulated barrier disc attachedto the central axle axial assembly and closely fit to the stationaryplenum to minimize air leakage between the insulated barrier disc andthe stationary plenum.
 4. The TCCEE as set forth in claim 3 furthercomprising an additional stationary plenum arranged around the surfacesof the compressor and condenser to collect and direct the air warmed bycompression and condensation.
 5. The TCCEE as set forth in claim 4further comprising a diverter assembly operatively connected with eachof the stationary plenum and the additional stationary plenum,constructed and arranged so that a destination and a source of hot airand cold air are interchangeable.
 6. The TCCEE as set forth in claim 1wherein the compressor includes a compressor shaft and a compressorshaft anchor attached to an independent motor shaft of the prime mover.7. The TCCEE as set forth in claim 6 wherein the compressor shaft anchoris interfaced into a planetary gear transmission driven from a centralaxial shaft to drive the compressor shaft at a speed multiple of thecentral axial shaft.
 8. The TCCEE as set forth in claim 1 wherein thefirst compressor stage comprises a shaft-driven mechanical compressorcoupled through a sealed shaft or magnetic coupling attached to astationary anchor.
 9. The TCCEE as set forth in claim 7 wherein themechanical compressor comprises a digital scroll compressor and theprime mover rotates at a constant speed.
 10. The TCCEE as set forth inclaim 1 further comprising a housing defining a window-mounted airconditioning unit.
 11. The TCCEE as set forth in claim 1 wherein therefrigerant comprises a high-molecular-weight refrigerant working fluidwith less than atmospheric pressure compressor suction conditions. 12.The TCCEE as set forth in claim 11 wherein the refrigerant comprises atleast one of R-123 or hydrofluoroolefin analogues intended forcentrifugal compressors
 13. A method for compressing, condensing,expanding and evaporating a refrigerant comprising the steps of:providing, in a first compression stage, isentropic adiabatic mechanicalcompression in the refrigerant, and providing, in a second compressionstage, isothermal centrifugal compression in radially expandingrefrigerant-filled conduits, in which the conduits are arranged insurfaces to induce heat transfer and a first air flow to remove heat ofcompression and condensation; receiving the compressed and condensedrefrigerant from the second compression stage, and that providesisentropic centrifugal expansion and isothermal expansion andevaporation in radially contracting conduits, the conduits beingarranged to induce a second air flow over surfaces of the condenser andevaporator; and rotating the conduits with a central axial assembly tosupply energy sufficient to compress refrigerant and circulate the firstair flow and the second air flow through the device.
 14. The method asset forth in claim 13 further comprising providing a stationary plenumto collect and direct the second air flow by the rotating action of thesurfaces of the condenser and evaporator, the surfaces of the condenserand evaporator defining blade-like conduits carrying refrigeranttherein.
 15. The method as set forth in claim 14 further comprisingproviding an additional stationary plenum arranged around the surfacesof the compressor and condenser to collect and direct the air warmed bycompression and condensation.
 16. The method as set forth in claim 15further comprising operating a diverter assembly operatively connectedwith each of the stationary plenum and the additional stationary plenum,constructed and arranged so that a destination and a source of hot airand cold air are interchangeable.
 17. The method as set forth in claim13 further comprising enclosing the conduits in a housing defining awindow-mounted air conditioning unit.